Revolving outer body arc vane rotary compressor or expander

ABSTRACT

Some implementations of this invention relate to energy systems and more particularly to rotating componentry enabling shaft work, propulsion drive, electric power generation, jet propulsion and/or thermodynamic systems related to aerothermodynamic thrust and shaft power, waste heat recovered shaft power, ventilation, cooling, heat, pressure and/or vacuum generating devices. Some implementations pertain to the art of vane assemblies for eccentrically placed rotating partial admission compressors and expanders that may either be used together or in conjunction with other mechanical, electrical, hydraulic and/or pneumatic machineries. Some implementations further relate to fluid energy recovery mechanical devices, targeting the field of gas turbine engines, internal combustion engines, furnaces, rotary kilns, coolers and refrigeration rotary components and/or expansion nodes. Other implementations are described.

FIELD OF THE INVENTION

This invention relates to energy systems and, in some implementations, more particularly to rotating componentry enabling shaft work, propulsion drive, electric power generation, jet propulsion and thermodynamic systems related to aerothermodynamic thrust and shaft power, waste heat recovered shaft power, ventilation, cooling, heat, pressure or vacuum generating devices. In some implementations, the invention mainly pertains to the art of vane assemblies for eccentrically placed rotating partial admission compressors and expanders that may either be used together or in conjunction with other mechanical, electrical, hydraulic or pneumatic machineries. Of particular interest, in accordance with come implementations, is the innovative fluid energy recovery mechanical devices targeting the field of gas turbine engines, internal combustion engines, furnaces, rotary kilns, coolers and refrigeration rotary components and expansion nodes.

BACKGROUND

There are many pivot vane and hinged vane rotary devices such as described in US patent and US patent application numbers U.S. Pat. No. 7,597,548 by Patterson, U.S. Pat. No. 7,117,841 by Kernes, U.S. Pat. No. 6,868,822 by Di Pietro, U.S. Pat. No. 6,125,814 by Tang, U.S. Pat. No. 5,692,887 by Krueger, U.S. Pat. No. 6,371,745 by Bassine, U.S. Pat. No. 5,616,019 by Hattori, U.S. Pat. No. 5,188,524 by Bassine, U.S. Pat. No. 5,163,825 by Oetting, U.S. Pat. No. 4,060,342 by Delmar, US 2003/0159673 by King, and U.S. Pat. No. 4,060,342 by Riffe; but it does not appear to Applicant that any of them exhibit a pivoting arc vane that is both hinged to a rotatable housing and the rotor as described herein. Most conventional vane rotary devices exhibit at least a few significant problems. As each vane slides back and forth within its respective slot, a considerable amount of friction, heat and wear can be generated. The sustained operation causes the vane slots to wear prematurely, leading to clearance increase and deterioration of performance. In some cases, the arc vane compressor and expander prevent such wear as explained in previous art [U.S. Pat. No. 8,579,615 by Akmandor].

SUMMARY

Some implementations of the invention relate to a rotatable pivoting arc vane (100, 126, 168, 174, 201) both hinged (98, 111, 125, 129, 192, 195, 197, 202) to a rotatable cylindrical housing (101, 134, 156, 157, 159, 161, 169, 173, 209) and a rotatable rotor (102, 139, 175, 205) placed within said cylindrical housing. Such configuration may be used either as a compressor (14, 47, 89) or an expander (4, 45, 76). In some implementations, the rotatable housing receives an eccentrically placed (106, 135, 152) rotor (102, 139, 175, 205) equipped by a single rocking arm (113, 193, 199) pivoting vane, all arranged around a fixed keyed (109) eccentric (106, 135, 152) shaft main axis (108). Between some implementations the housing and the rotor, depending on the rotational position of the rotatable pivoting vane, forms a single (104,133) or a plurality of working chambers (121, 123, 143, 148, 190, 191, 203, 206, 215, 217, 218, 219) each of the said chambers, delimited by inner cylindrical peripheral surface (110) of main housing, the outer peripheral surface (107) of the rotor and the side surfaces (120, 122) of the hinged arc vane. Because some rotary vane compressors or expanders are partial admission devices, some such devices have low mass flow rate requirements and they become extremely useful when used in conjunction with well established power systems such as gas turbine engines, internal combustion engines, inner and/or outer running electrical motors.

Some friction-free and wear-free simple arc vane mechanism resemble the reliable rolling piston type rotary vane compressors and expanders widely used in the refrigeration industry for decades. In accordance with some embodiments, the described apparatus provides an improved rotary compressor or rotary expander that has a rotatable (115, 141, 150) housing and an inner rotor (114, 140, 151) both linked with a durable, wear resistant, friction-free pivoting hinged single arc vane.

The novelty behind some implementations of such expander and compressor performance can be summarised as follows: instead of using a full admission turbine like radial or axial inflow turbines, in some implementations, a partial admission high torque rotary vane expander is used, requiring a relatively low mass flow rate throughput. In some implementations, the large flow rate turbine is replaced by an expander having one order of magnitude less mass flow rate and allowing high expansion in hermetic volume. In accordance with some implementations, an arc vane expander has a very efficient and robust aerothermodynamic architecture able to accept high temperature, high pressure working fluids. Arc vane compressor has a no-stall capability allowing to reach high pressure ratio with low mass flow throughput. Other features, advantages, and applications of the invention will be apparent from the following descriptions, the accompanying figures, and from the claims.

Some implementations of the rotary components described herein are configured to be an efficient alternative to the sliding vane turbo-rotary components of turbo-engines described in previous art [U.S. Pat. No. 7,314,035 by Akmandor and al., FIGS. 8-9-10]. Some implementations of the present invention further address some additional problems related with; a) eccentricity related low shaft torque output, b) friction between rotor and side wall, c) surface wear, d) pressure seal, e) rotor imbalance caused by eccentricity, f) rotor aerodynamic drag, and/or g) impairing caused by sudden pressure expansion at expander inlet prior to chamber expansion. Some of these weaknesses limit the performance and wide use of arc vane rotary compressor and expanders. Some implementations of the described claims and novel devices aim to eliminate aforementioned difficulties and increases thereafter described system performance.

BRIEF DESCRIPTION OF THE DRAWINGS

In order that the manner in which the above recited and other features and advantages of the present invention are obtained, a more particular description of the invention will be rendered by reference to specific embodiments thereof, at least one of which is illustrated in the appended drawing. Understanding that the drawing depicts only typical embodiments of the present invention and is not, therefore, to be considered as limiting the scope of the invention, the present invention will be described and explained with additional specificity and detail through the use of the accompanying drawing in which:

FIG. 1: Schematic view of a turboshaft or turboprop engine equipped with a waste heat recovery booster compressor system, in accordance with some embodiments;

FIG. 2: Schematic view of a turboshaft or turboprop engine equipped with a waste heat recovery shaft power assist system, in accordance with some embodiments;

FIG. 3: Schematic view of a waste heat recuperated turbo-rotary compound engine, in accordance with some embodiments;

FIG. 4: Schematic view of a revolving outer body arc vane rotary expander, in accordance with some embodiments;

FIG. 5: Schematic view of a revolving outer body arc vane rotary expander equipped with inlet and outlet ports, in accordance with some embodiments;

FIG. 6: Schematic view of a counter-revolving outer body arc vane rotary compressor at beginning of compression process, in accordance with some embodiments;

FIG. 7: Schematic view of a counter-revolving outer body arc vane rotary compressor towards an end of a compression process, in accordance with some embodiments;

FIGS. 8A-8C: Schematic view of a side, front and perspective views of a fully balanced, twin, counter-revolving outer body arc vane rotary compressor, in accordance with some embodiments;

FIG. 9: Exploded view of fully balanced, twin, counter-revolving outer body arc vane rotary compressor, in accordance with some embodiments;

FIG. 10: Schematic view of a continuos flow revolving outer body rotary expander with two radially nested arc vanes operating in series (first quarter expansion already past), in accordance with some embodiments; and

FIG. 11: Schematic view of a continuos flow revolving outer body rotary expander with two radially nested arc vanes operating in series (third quarter expansion about to be completed), in accordance with some embodiments.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS

Some embodiments of the described invention are configured to realise high compression ratios within fully hermetic compressor volumes with minimum pressure and mass flow leakage and to generate high torque in expanders following a long power extraction phase. Some embodiments are further configured to provide a hinged arc vane type link between a main rotatable housing and a rotor eccentrically placed within said housing. Some embodiments are depicted in FIGS. 4 and 5 and serve multipurposes: firstly, in accordance with some embodiments, pressure difference across vane side surfaces (120, 122) generates force and torque across working chambers (121 and 123 or 143 and 148, 190 and 206, 191 and 203, 215 and 219, 217 and 218). Secondly, in accordance with some embodiments, arc vane is acting as driving linkage between outer rotatable housing (115, 141, 150) and eccentrically housed rotor (114, 140, 151). The above and other distinctive novel features of some embodiments of the present invention will be apparent from the following detailed description of specific embodiments of the apparatus when read in conjunction with the accompanying drawings, wherein:

FIG. 1 depicts schematic view of a representative embodiment of a turboshaft or turboprop engine equipped with a waste heat recovery booster compressor system. In accordance with some embodiments, a turboprop or turboshaft engine comprises compressor (6), combustor (24), high pressure turbine (9), low pressure turbine (11) and exhaust (16). In some embodiments, fuel (26) is pumped (25) to (27) combustor (24) to burn with main airflow. Specifically, in some embodiments, main airflow path is thraced through numbered arrows (1, 32, 31, 28, 23, 10, 21, 18). In some cases, the high pressure spool compressor (6) and turbine (9) are connected by shaft (7). The turboprop or turboshaft loads are connected, in some embodiments, at low pressure shaft (8) end (33). To increase both shaft power output and thermal efficiency, a waste heat recovered booster compressor system is added to some embodiments of the system. In some embodiments, the majority of the exhaust waste heat is not absorbed by the engine main flow (1, 32, 31, 28, 23, 10, 21, 18) but by a secondary stream (13, 20, 15, 17, 19, 22, 29, 30, 5) with a much smaller mass flow rate. In some cases, the two flow streams do not mix with each other. Additionally, in some embodiments, the secondary novel flow stream (13, 15, 17, 19, 22, 29, 30, 5) is first pressurised by rotary compressor (14) driven (12) by low pressure turbine (11). Moreover, in some embodiments, secondary stream is heated up while flowing through compact once-through spiral exhaust heat exchanger (15, 17, 19). There, exhaust waste heat of main flow (18) is substantially recovered and high temperature, high pressure secondary flow thereafter expands through a rotary turbine (4) that assists to drive (3) main flow booster compressor (2).

FIG. 2 depicts schematic view of a representative embodiment of a turboshaft or turboprop engine equipped with a waste heat recovery shaft power assist system. In accordance with some embodiments, a turboprop or turboshaft engine comprises compressor (36), combustor (63), high pressure turbine (39), low pressure turbine (43) and exhaust (50). In accordance with some embodiments, fuel (65) is pumped (64) to (66) combustor (63) to burn with main airflow. In some such embodiments, main airflow path is traced through numbered arrows (34, 35, 69, 68, 67, 62, 61, 60, 40, 41, 42, 51). Additionally, in some embodiments, high pressure spool compressor (36) and turbine (39) are connected by shaft (37). Turboprop or turboshaft engines load are connected, in some embodiments, at low pressure shaft (71, 70, 38, 59, 58) end (72). To increase both shaft power output and thermal efficiency, in some embodiments, a waste heat recovered shaft power assist system is added. In some embodiments, the exhaust waste heat is absorbed by a secondary stream (46, 48, 49, 53, 54, 57, 56, 52) having a much smaller mass flow rate. In some embodiments, the two flow streams do not mix. In some embodiments, secondary novel flow stream is first pressurised by rotary compressor (47) and is heated up while flowing through compact once-through spiral exhaust heat exchanger (48, 49, 53, 54). There, in some embodiments, exhaust waste heat of main flow (51) is recovered and high temperature, high pressure secondary flow thereafter expands through a rotary turbine (45). Furthermore, in some embodiments, generated rotary turbine power assists in driving the load through extended shaft (55, 44). Waste heat recovered turboprop or turboshaft engine is safer and more reliable as shaft power is produced through two separate air streams (primary stream: 34, 69, 68, 67, 62, 61, 60, 40, 41, 42, 51 and secondary stream: 46, 48, 49, 53, 54, 57, 52). At off design phases of flight like aircraft climb and acceleration phases, exhaust (50) heat is typically higher, and contrary to some conventional turboprop engines, the shown novelty of some embodiments will continue to provide a unique and reliable near “design-point” (cruise phase) high shaft power output. Waste heat secondary air stream, when subjected to higher elevated exhaust temperatures, generates higher power. Thus, in some embodiments, contribution of waste heat secondary stream is higher when more power is demanded by aircraft. No-stall characteristic of closed volume arc vane compressor and turbine also supports depicted engine performance. If additional fuel line (78), pump (77) and initial spark ignition (SI) system (79) is provided to rotary turbine (45, 76), it is possible, in accordance with some embodiments, to directly power boost the power shaft (72, 71, 70, 38, 59, 58, 44, 55) by using the rotary compressor (46) and the rotary turbine (45) as an efficient provisionary alternative small engine. This alone can increase the safety and reliability of a conventional turboprop and/or turboshaft engine.

FIG. 3 depicts a different representative embodiment representing a schematic view of a waste heat recuperated turbo-rotary compound engine. In accordance with some embodiments, the main flow streams through the turbo components and is traced through numbered arrows (97, 96, 95, 88, 85). In some embodiments, a separate secondary flow streams through rotary components and is traced through numbered arrows (81, 90, 86, 83, 80, 75). In some such embodiments, both streams never meet and mix. Main airflow is pressurised by compressor (73) and is mixed and burned with fuel (93) pumped (92) into (94) combustion chamber (91). In some embodiment, hot main flue gas is expanded by turbine (87) and generated power drive (82) a rotary compressor (89). In some embodiments, rotary compressor pressurises secondary air stream that is heated up while flowing through compact once-through spiral exhaust heat exchanger (83). In some embodiments, exhaust (84) waste heat of main flow (85) is recovered. High temperature, high pressure secondary flow thereafter expands through a rotary turbine (76). As an option, the secondary flow may receive fuel (78) pumped (77) into rotary turbine combustor (79). Secondary flow and fuel mix burns inside some embodiments of said combustor (79) and/or inside the rotary expander (76). In some embodiments, generated power drives (74) main flow compressor (73). This turbo-rotary jet engine has superior performance compared to some conventional turbojet engines as some of its embodiments have better stall margin, high thrust power and/or high thermal efficiency. Some embodiments of rotary compressor (89) require about 30% less power when compared to some conventional axial or radial compressors and more turbine (87), and, in some embodiments, power is left for producing exhaust (84) thrust. Some embodiments of rotary turbine (76) can operate at higher inlet pressures and temperatures with regards to some conventional axial or radial turbines. Accordingly, in some instances, secondary stream is proportionally smaller and rotary components (89, 76) are more compact and lighter.

FIG. 4: depicts top view of a representative embodiment of a revolving outer body arc vane rotary expander. In accordance with some embodiments, circularly cylindrical rotor (102) is rotatably and eccentrically mounted within a rotatable housing (101). In some such embodiments, said rotor (102) is rotating around its axis centre (106) and the rotatable housing (101) is rotating around its axis centre (108). In some embodiments, circumferential speeds of rotor outer diameter and rotatable housing inner diameter is same at common tangency point (99). At this circumferential position, arc vane (100) is shown to be fully retracted within rotor housing. In some embodiments, rotatable rotor axis (106) and rotatable housing axis (108) are fixed, allowing any lubrication and cooling lines (not shown) to be brought to rotor bearing (105, 131, 211) and rotatable housing bearings (165). In accordance with some embodiments, hinged arc vane (100) is pivoting around pivot rod (111) secured to the rotatable rotor. In shown time snapshot, only one crescent shape working chamber (104) is formed. Fluid is filling this crescent shape cavity. Fluid is either air, or any other working gas or vapour, or any other liquid-vapour mixture. In some embodiments, rotatable side plates (166, 170, 172, 176) are securely bolted (or otherwise connected) to rotatable housing (101) via bolt holes (103, 112) (and/or another suitable mechanism) providing a hermetic enclosure with leaks.

FIG. 5 depicts a different time snapshot of same embodiment shown in FIG. 4 for some embodiments of a revolving outer body arc vane rotary expander equipped with non-revolving inlet (116) and rotatable outlet (124) ports. In accordance with some embodiments, as the arc vane (100) cuts through the crescent-shape working volume, a plurality of working chambers (123, 121) are sequentially created within the crescent shaped cavity (104) delimited by rotor outer cylindrical surface (107), rotatable housing inner cylindrical peripheral (110) and vane arched side surfaces (120, 122). In some embodiments, first working chamber (121) accepts high pressure working fluid that enters through intersecting area of non-revolving inlet port (116) and portion (117) of crescent shape revolving working chamber. In some embodiments, pressure difference between working chambers (121 and 123) creates a pushing force acting on exposed arc vane surface. Exhaust port (124) of such rotary expander is, in some embodiments, continuously allowing expanded low pressure flow to discharge. While rotatable housing (115) and rotor (114) are revolving around their respective centers (108 and 106), the arc vane is, in some embodiments, performing a swinging arc motion with arm (113) extending from hinge (111) and sweeping area (119) within rotor. In some such embodiments, arc vane moves tangentially to arc slot (118) boundary with little to no friction.

In accordance with some embodiments, a rotary compressor unit is similar in component to the expander unit but the rotational direction and the inlet and exit port are reversed. Indeed, in some embodiments, expander has a clockwise rotation and non-revolving port (116) is fluid inlet and revolving port (124) is fluid exit. For compressor operation, in some embodiments, rotation is counterclockwise and ports are interchanged: now, revolving port (124) is fluid inlet and port (116) is fluid exit.

FIG. 6 depicts a representative embodiment of counter-revolving outer body arc vane rotary compressor. In this figure, both rotatable housing (134) and rotor (139) housed eccentrically within said housing revolves counterclockwise (141 and 140, respectively). Time snapshot at beginning of compression process is shown. Said rotor is circumferentially housed within a rotatable cylindrical housing also rotating counterclockwise (141) around fixed main shaft center axis (149). The arc vane (126), in this non-limiting illustration, is rigidly connected to the pivoting rod (125) through arm (113). The arc vane (126), in this Figure, engages across its entire height (198) inside the rotatable housing (134). The arc vane is slidingly assembled and hinged (125) to rotatable housing and also articulatingly (129) mounted to rotor (139). The extent of tangency of the vane-rotor articulation (129) covers a circular arc in excess of 181° (or any other suitable angle), arc vane hinge cannot disengage from rotor cylindrical cavity (167) during working operation of the unit. In some embodiments, the two hinged ends (125 and 129) of arched vane are contoured and positioned in a way to allow pivoting motion of the arc vane during 360° rotation of the eccentric rotor (139) and the rotatable housing (134). In some embodiments, the angular speeds of said rotatable housing and said rotor are different but since there is a small clearance at the common tangency point (127) of two osculating surfaces, namely the rotor outer cylindrical boundary (107) and the rotatable housing cylindrical inner peripheral (110), there is little to no shear friction. In some embodiments, the crescent shape volume (133) is filled through fluid entering from inlet port (128) from outside volume (132). In some embodiments, a periodic sequence of compressed fluid is discharged from the outlet port (142) with each rotation of the eccentric rotor and rotatable housing in response to input driving torque and circumferential speed of main rotor shaft. In some embodiments, the rotor axis centre (135) is fixed to outer casing (130), casing is also fixed to horizontal frame (137). In some such embodiments, there are circumferentially 8 bolt (or other fastener) holes (138) on the outer casing fixing compressor modules together. In accordance with some embodiments, rotor (139) is journalled in bearing (131) centered at fixed center axis (135). Additionally, in some embodiments, clearance (136) is left between rotor outer circumferential radius (107) and fixed outer casing (130).

FIG. 7 depicts the same embodiment illustrated in FIG. 6 at a different time snapshot. Counter-revolving outer body arc vane rotary compressor is depicted here, in accordance with some embodiments, towards the end of compression process. In this Figure, rotor is rotating counterclockwise (151) around its fixed axis center (152) which is eccentrically displaced from rotatable housing fixed shaft axis center (149). As rotatable housing is, in some embodiments, driven counterclockwise by an external motor—not shown—the rotary compressor breathes from external source (145) through the rotatable intake (146). First working chamber (148) is receiving the fluid from rotatable intake port (147), said fluid is either air, or any other working gas or vapour, or any other liquid-vapour mixture. As arc vane (126) cuts, in some embodiments, through the crescent-shape working volume (133), a plurality of working chambers (148, 143) are sequentially created within the crescent shaped cavity. In some such embodiments, the first working chamber (148) accepts low pressure working fluid and the second working chamber (143) compresses the working fluid which was admitted within the housing by the first chamber (148) in the precedent 360° rotation of housing and eccentric rotor. Said fluid is, in some embodiments, compressed by a continuously diminishing chamber working volume (143) discharging to outlet port (144). In some cases, exhaust port (144) of such rotary compressor is equipped with a check valve or a rotating valve—not shown—that allows flow to discharge from rotary compressor device but strictly prevents any flow intake from exhaust port (144). In some embodiments, the rotary expander unit is similar in component to the compressor unit but its geometric size is different and the direction of rotation is now clockwise. In some embodiments, the ports are also interchanged: inlet port is (144) and exit port is (147). With the beginning of a new working cycle, some embodiments of the first working chamber (143) admit high pressure fluid from inlet port (144) and the working fluid expands in said chamber (143) as the eccentric rotor (139) and rotatable housing (134) revolve under the forcing torque and pressure of admitted fluid. In the consecutive 360° clockwise rotation which defines the second working cycle, the fully expanded working fluid which is now in the second working chamber (148) discharges, in some embodiments, through rotatable exhaust port (147). In some embodiments, under the rotational action of the eccentric rotor and rotatable housing, the working chambers (143, 148) continuously change size and volume. The expansion pressure ratio of expander is dependent on working fluid inlet pressure, the amount of the mass flow through said expander and the maximum crescent shape working volume of said expander unit.

FIGS. 8A-8C depict representative embodiments of side, front and perspective views of fully balanced, twin, counter-revolving outer body arc vane rotary compressor. In some embodiments, there are two revolving units (159, 161) working symmetrically with respect to rotatable housing center. In some such embodiments, all components in the second unit (159, 156) are displaced by 180° out of phase to respective components of first unit (161, 157). As such, in some embodiments, the inlet port of second unit is placed at about 180° out of phase from inlet port (160) of first unit (161, 157). Rotor bearing housings for first and second compressor unit are denoted by (162, 158) respectively and their eccentricity, in accordance with some embodiments, is also shown to be about 180° out of phase (162, 158) with respect to each other. The fixed non-rotating components are housing plates (163, 153, 154 and 155).

FIG. 9 shows an exploded view of the same embodiment in FIGS. 8A-8C. In FIGS. 8A-9, the circumferential position of the arc vanes (168, 174) are illustrated as being about 180° out of phase with each other as well as the rotatable housings (169, 173) and the rotors (175) with hinge groove (167). In some embodiments, the rotatable side plates (166, 170, 172, 176) hermetically close the compressor working chambers, thus substantially, if not completely, eliminating leakage. In some embodiments, at rotor shaft end, bearings (165, 162, 158) and lubrication means (not shown) allow rotor rotation with minimum friction. In some such embodiments, bearings (165, 162, 158) are supported on their outside diameter by outer fixed side plates (164, 171, 177) that are rigidly connected to horizontal fixed reference support (178).

FIG. 10 depicts a representative embodiment of a continuos flow revolving outer body rotary expander with two radially nested arc vanes (inner: 193, outer: 201) systems operating in series. In some embodiments, pressurised fluid enters continuously through rotor fixed shaft axis centre (212). In accordance with some embodiments, the clockwise revolving inner rotor (205) is eccentrically (204) displaced from rotatable middle cylindrical ring (187) in such a way that the rotor (205) is always in tangent to the cylindrical ring (187) at osculating common surface tangency point (186). In some embodiments, the labyrinth concentric circle seals (208) prevent pressurised working fluid contained in the hollow fixed main shaft center from leaking. Rotor bearings (211) and rotor bearing housing (207, 210) are mounted, in some embodiments, around fixed rotor axis center (212). Additionally, in some embodiments, the inner arc vane (193) is sealingly extending from inner rotor slot (194) and is hinged (192) both to inner rotor and middle cylindrical ring (195) to divide the crescent shape volume into two consecutive inner working chambers (190, 206). In some embodiments, the working fluid continuously enters first working chamber (190) through radial connection channel (188). This channel can take any other cross sectional shape so as to decrease aerothermodynamic total pressure loss and increase fluid kinetic energy along said channel. In some embodiments, the outer arc vane (201) is sealingly extending from rotatable housing slot (198, 200) and is hinged (202, 197) to middle cylindrical ring (187) and rotatable outer housing (209) to divide the outer crescent shape volume into two consecutive outer working chambers (191, 203). In accordance with some embodiments, pressure in first working chamber (190) is higher or equal to pressure in second working chamber (206) as this second chamber discharge pressurised fluid to third working chamber (191) through connection port (196). This connection port can be an aerodynamic port with convergent and/or divergent profiling contours so as to minimise total pressure loss and increase fluid kinetic energy. In some embodiments, the third working chamber (191) is located at a higher radius where expansion against the outer arc vane (201) occurs. In some embodiments, pressure in the fourth and last working chamber (203) is at a low reference level as said working chamber exit port (182) is regularly or always open. Reference low level pressure may be atmospheric as it is the case for an open thermodynamic cycle or any fixed low value in a closed thermodynamic cycle such as found in organic Rankine cycles or Rankine cycles. In some embodiments, the osculating common tangency point between rotatable main housing (209) and rotatable middle ring (187) has a fixed position (185) and does not circumferentially change with time. In some embodiments, the fourth working chamber (203) intersects (183) at all time with exit port (182) allowing this working chamber to always stay at low reference pressure. The inner and outer arched vanes (193, 201), in accordance with some embodiments, are sealingly moving along their respective circular arc path (118). In some embodiments, arched vanes each have a pivot axis (192, 197) respectively fixed to rotor (205) and rotatable housing body (209). Pivoting arm (199) operating inside a cavity (198, 200) in response to the 360° rotations of outer housing (209), middle ring (187) and inner eccentric rotor (205). In some such embodiments, common tangency points (185, 186) are on top of each other. In other embodiments, however, this may not be the case. Bolt (or other fastener) holes (189, 184) on rotatable middle ring (187) and on rotatable outer housing (209) allow some embodiments of the side plates (not shown) to hermetically seal the inner and outer working chambers so as to avoid any fluid leakage to outside. In some embodiments, concentric labyrinth seals (181) also help prevent such leaks. Inner eccentric rotor (205), rotatable middle ring (187) and rotatable outer housing (209) have, in some embodiments, different angular speeds and it is still possible to hermetically seal said components and associated arc vanes (193, 201) with a multitude of concentric, leak-proof fixed and rotatable side plates (166, 170, 172, 177) separatedly bolted through indicated holes (184,189) to said components (205, 187, 209). In another embodiment, it is also possible to hermetically seal inner rotor (205), rotatable middle ring (187) and rotatable outer housing (209) and associated arc vanes (193, 201) with a single side plate sealingly bolted using circumferentially distributed bolt (or other fastener) holes (184). Fluid leaks from said side plates surfaces are prevented, in some embodiments, using concentric circumferential labyrinth seals. Rotatable main housing (209) may also be fully enclosed with a fixed circumferential housing (179) bolted through holes (180) to fixed side plates (164, 171, 177).

FIG. 11 depicts a time snapshot of a representative embodiments showing a continuos flow revolving outer body (209) rotary expander with two radially nested arc vanes (193, 202) operating in series. This is the same expander depicted in FIG. 10 but shown at a different time frame where three-quarter of total volume (217 and 219) expansion is about to be completed. In some embodiments, the inner system is mainly composed of an inner rotor (205), a rotatable middle ring (187) and an arc vane (193) movably connected to respective rotatable components (205, 187). This inner system receives, in some embodiments, continuos fluid flow through fixed inlet tube (213) and passes on to the first working chamber (215) via a continuos fluid transfer tubing (214). The role the first inner arc vane (193) is to partition this incoming fluid into sequential batches of working volume (215, 219). In some embodiments, the partitioning is achieved each time the inner arc vane (193) pivot point (195) revolves and crosses the common fixed tangency point (186). The first working chamber (215) pressure is higher or equal to second working chamber (219) pressure. Thus, in some embodiments, inner system forces the inner arc vane to rotate clockwise at virtually all times of operation. Torque and power performance belongs to inner system and is entitled as power torque phase. In some embodiments, working fluid in second working chamber (219) then crosses into third working chamber (217) through a transfer port (216) situated between second and third working chambers (219, 217). There, working volumes (219, 216 and 217) expands all together until the fluid passage (216) is tangent to osculating common tangency point (186). Although total expanding volume (219, 216, 217) is getting larger, pressure of third working volume (217) is, in some embodiments, larger than pressure of fourth working volume (218) as said volume is always open to atmosphere via exit port (220). As working fluid expands, pressure difference across the outer arc vane (201) forces some, if not all, rotatable components to rotate as well. Namely, outer arc vane (201) forces the outer rotatable housing (209) to rotate, also forcing the rotatable middle ring (187) to revolve around its own fixed center axis.

Some preferred turbo engine embodiments are depicted in FIGS. 1, 2 and 3, but there is a multitude of other possible combination to utilise state-of-the-art radial, axial compressor and turbine blades, fan blades, propeller blades, helicopter rotor blades and connect them on the outer periphery of rotatable housing of described rotary expanders or rotary compressors so as to form turbo-rotary components. These novel components are to be used as part of turbo-ramjets, turbojets, turbofans, turboprops and/or turboshaft engines. It is also possible to utilize state-of-the-art electrical generators (not shown) and electrical motor components (not shown) connected on the outer periphery of rotatable housing of described radially nested multistage rotary expander or rotary compressors so as to form compact fluid energy recovery electrical generator devices or hybrid electric engine devices. Although specific features of the invention are shown in some drawings and not others, this is for convenience only as each feature may be combined with any or all of the other features in accordance with the invention. Other embodiments will occur to those skilled in the art and are within the following claims: 

1. A rotary expander, comprising: a rotatable housing having a generally cylindrical main chamber, a generally cylindrical rotatable rotor mounted eccentrically with respect to housing main chamber axis center; a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotatable housing body and a hinge movably connecting said vane to rotor, or alternatively, a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotor body and a hinge movably connecting said vane to the rotatable housing body, the rotary expander further including: a fixed shaft center rigidly connected to external fixed reference frame and a rotatable housing revolving 360° around said fixed axis center; a fixed shaft center rigidly connected to eccentrically placed fixed cylindrical shaft extension and a rotor rotatably and circumferentially revolving 360° around said eccentrically placed cylindrical shaft extension; air and/or fluidic journal and/or roller bearings provided between rotatable housing and fixed shaft center and also provided between rotor and fixed eccentric shaft to reduce rotational friction; a single arc vane element pivotally mounted to rotor body and periodically extending sealingly from rotor slot into said rotatable main chamber to divide the crescent shape volume into two consecutive working chambers, said rotor movably hinged to said arc vane in such a way that outer cylindrical surface of said rotor is sealingly tangent to rotatable housing working chamber inner peripheral without any frictional contact, or alternatively, a single arc vane element pivotally mounted to rotatable housing body and periodically extending sealingly from rotatable housing slot into eccentrically placed rotor to divide the crescent shape volume into two consecutive working chambers, said rotatable housing body movably hinged to said arc vane in such a way that inner cylindrical surface of said rotatable housing is sealingly tangent to rotor working chamber outer peripheral without any frictional contact; a crescent shape rotatable housing working chamber formed by inner peripheral of housing and outer surface of the rotor being periodically divided into at most two working chambers by the pivoting vane and the common tangency point of two osculating surfaces, namely the rotor outer boundary and rotatable housing cylindrical inner peripheral; a plurality of working chambers formed depending on the rotational position of the pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable housing chamber, outer peripheral surface of the rotor and the side surface of the hinged arc vane; an inlet port regulating the admission time and duration of the entering working fluid within rotary expander and thus preventing the said working fluid to bypass the working chambers and shortcut the inlet and outlet ports; an inlet port formed in said rotatable housing for admitting high pressure and momentum inlet fluid flows into the working chamber delimited by the rotor side surface, rotatable housing cylindrical peripheral walls and the arc vane side surface; a working cycle lasting for 360° clockwise or counterclockwise rotation of rotatable housing, wherein a new working cycle under the rotation of said housing is initiated every time the arc vane crosses said tangency point, wherein a first working chamber admitting high pressure fluid from inlet port and expansion of the working fluid in said chamber imparts energy to said rotatable housing, eccentric rotor and arc vane assembly under the forcing torque and pressure of admitted fluid, and wherein said working chamber is progressively enlarged to a crescent shape like volume and expanding the admitted high pressure and momentum working fluid through; a second working cycle defined in the consecutive 360° clockwise or counterclockwise rotation of said rotatable housing, eccentric rotor and arc vane assembly allowing the fully expanded working fluid now in second working chamber to discharge through exhaust port, wherein the maximum crescent shape volume of the expander main chamber is sized to allow the inlet fluid pressure expansion to desired discharge pressure; a periodic sequence of expanded fluid expulsed from the outlet port with each rotation of rotatable housing, eccentric rotor and arc vane assembly in response to high pressure and temperature fluid expansion in consecutive working chambers of said expander; a dynamic balance achieved by assembling and operating side-by-side twin/identical rotary expanders with separate inlet and exit ports, said twin expanders connected in such a way that one rotary expander respective arc vane circumferential positions has a 180° phase angle with respect to other twin expander; radial or axial compressor blades or fan blades attached on the outer periphery of rotatable housing of described rotary expander so as to form turbo-rotary components to be used as part of turbojets, turbofans, turboprops and turboshaft engines; and electrical generators components attached on the outer periphery of rotatable housing of described rotary expander so as to form a compact fluid energy recovery electrical generator device.
 2. A nested multistage rotary expander combining a plurality of radially nested (first/inner and second/outer) rotary expanders in such a way that the output of first/inner rotary expander is the input of a second/outer rotary expander, wherein the first and second rotary expanders comprising: a rotatable housing having a generally cylindrical main chamber, a generally cylindrical middle ring mounted eccentrically with respect to rotatable housing main chamber center and a generally cylindrical rotatable rotor mounted eccentrically with respect to rotatable middle ring, the rotatable housing chamber fully containing the rotatable middle ring and the rotatable middle ring fully containing the rotor; radially nested multistage rotary expander further including: a generally cylindrical rotor free to revolve 360° around fixed eccentrically placed axis center, a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotor and a hinge movably connecting said vane to rotatable middle ring, said middle ring eccentrically placed axis center located closer to main rotatable housing axis center with respect to rotor axis center; a generally cylindrical rotatable housing free to revolve 360° around fixed axis center and a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotatable housing and a hinge movably connecting said vane to rotatable middle ring; a fixed shaft center rigidly connected to external fixed reference frame and a rotatable housing revolving 360° around said fixed shaft center; a fixed shaft center rigidly connected to eccentrically placed fixed cylindrical fixed shaft extension and a middle ring, rotatably and circumferentially revolving 360° around said eccentrically placed cylindrical fixed shaft extension; a fixed shaft center rigidly connected to eccentrically placed fixed cylindrical axis extension and a rotor rotatably and circumferentially revolving 360° around said eccentrically placed axis extension, an eccentricity of rotor axis being larger than eccentricity of rotatable middle ring axis; air and/or fluidic journal and/or roller bearings provided between rotatable housing and fixed shaft center, between rotatable middle ring and fixed eccentric shaft axis and also between rotor and fixed eccentric rotor shaft axis to reduce rotational friction; an inner single arc vane element pivotally mounted to rotor body and periodically extending sealingly from rotor slot into said rotatable middle ring to divide the inner crescent shape volume into two consecutive working chambers, said rotor movably hinged to said inner arc vane in such a way that outer cylindrical surface of said rotor is sealingly tangent to rotatable middle ring chamber inner peripheral without any frictional contact; an outer single arc vane element pivotally mounted to rotatable housing body and periodically extending sealingly from rotatable housing slot into eccentrically placed rotatable middle ring to divide the outer crescent shape volume into two consecutive working chambers, said rotatable housing body movably hinged to said outer arc vane in such a way that inner cylindrical surface of said rotatable housing is sealingly tangent to rotatable middle ring working chamber outer peripheral without any frictional contact; an inner crescent shape middle ring chamber formed by inner peripheral of middle ring and outer surface of rotor being periodically divided into at most two working chambers by the pivoting inner vane and the common tangency point of two osculating surfaces, namely the rotor outer boundary and rotatable middle ring cylindrical inner peripheral; an outer crescent shape main housing chamber formed by inner peripheral of main housing and outer surface of middle ring being periodically divided into at most two working chambers by the pivoting outer vane and the common tangency point of two osculating surfaces, namely the middle ring outer boundary and rotatable main housing cylindrical inner peripheral; a working cycle lasting for 360° clockwise rotation of rotatable middle ring, wherein a new working cycle under the rotation of said middle ring is initiated every time the inner arc vane crosses the tangency point, wherein a first working chamber admitting high pressure fluid from inlet port and filling said chamber imparts energy to said rotatable middle ring, eccentric rotor and inner arc vane assembly under the forcing torque and pressure of admitted fluid, and wherein said first working chamber is progressively enlarged to a crescent shape like volume with admitted high pressure and momentum working fluid to be moved to a second working chamber; a working cycle lasting for 360° clockwise rotation of rotatable main housing, wherein a new working cycle under the rotation of said main housing is initiated every time the outer arc vane crosses the tangency point, wherein a third working chamber admitting high pressure fluid from connected second working chamber imparts energy to said rotatable main housing, eccentric rotor and outer arc vane assembly under the forcing torque and pressure of admitted fluid, and wherein a third working chamber is progressively enlarged to a crescent shape like volume and expanding the admitted high pressure and momentum working fluid through; a second working cycle defined in the consecutive 360° clockwise rotation of said rotatable housing, eccentric middle ring and outer arc vane assembly allowing the fully expanded working fluid to be moved to fourth working chamber to discharge through exhaust port, wherein the maximum crescent shape volume of the outer expander main chamber is sized to allow the inlet fluid pressure expansion to desired discharge pressure; a plurality of working chambers formed depending on the rotational position of the inner pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable middle ring, outer peripheral surface of the rotor and the side surface of the inner hinged arc vane; a plurality of working chambers formed depending on the rotational position of the outer pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable main housing, outer peripheral surface of the middle ring and the side surface of the outer hinged arc vane; an inlet port for inner rotary expander located at rotor fixed axis center, continuously admitting working fluid within inner rotary expander, an inner arc vane preventing said working fluid to bypass the inner working chambers and shortcut inner expander inlet and outlet ports; an inlet port for outer rotary expander located on the rotatable middle ring, continuously admitting working fluid from inner rotary expander working chamber, the outer arc vane preventing said working fluid to bypass the outer working chambers and shortcut outer expander inlet and outlet ports; both inner and outer inlet ports admitting high pressure and momentum inlet fluid flows into the working chambers delimited by the rotor, rotatable middle ring, rotatable housing cylindrical peripheral walls, inner and outer arc vanes, respectively; a periodic sequence of expanded fluid expulsed from the outlet port with each rotation of rotatable housing, rotatable middle ring and outer arc vane assembly in response to high pressure and temperature fluid expansion in consecutive working chambers of said outer expander; a dynamic balance achieved by assembling and operating side-by-side twin/identical radially nested multistage rotary expanders with separate inlet and exit ports, said twin expanders connected in such a way that each expander respective outer vane circumferential positions is 180° phase angle apart with respect to other twin expander; radial or axial compressor blades or fan blades attached on the outer periphery of rotatable housing of described radially nested multistage rotary expander so as to form turbo-rotary components to be used as part of turbojets, turbofans, turboprops and turboshaft engines; and electrical generators components attached on the outer periphery of rotatable housing of described radially nested multistage rotary expander so as to form a compact fluid energy recovery electrical generator device.
 3. A rotary compressor, comprising: a rotatable housing having a generally cylindrical main chamber, a generally cylindrical rotatable rotor mounted eccentrically with respect to housing main chamber center axis; a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotatable housing body and a hinge movably connecting said vane to the rotor, or alternatively, a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotor body and a hinge movably connecting said vane to the rotatable housing body, the rotary expander further including: a fixed shaft center rigidly connected to external fixed reference frame and a rotatable housing revolving 360° around said fixed axis; a fixed shaft center rigidly connected to eccentrically placed fixed cylindrical shaft extension and a rotor rotatably and circumferentially revolving 360° around said eccentrically placed cylindrical fixed shaft extension; air and/or fluidic journal and/or roller bearings provided between rotatable housing and fixed shaft center and also provided between rotor and fixed eccentric shaft to reduce rotational friction; a single arc vane element pivotally mounted to rotor body and periodically extending sealingly from rotor slot into said rotatable main chamber to divide the crescent shape volume into two consecutive working chambers, said rotor movably hinged to said arc vane in such a way that outer cylindrical surface of said rotor is sealingly tangent to rotatable housing working chamber inner peripheral without any frictional contact, or alternatively, a single arc vane element pivotally mounted to rotatable housing body and periodically extending sealingly from rotatable housing slot into eccentrically placed rotor to divide the crescent shape volume into two consecutive working chambers, said rotatable housing body movably hinged to said arc vane in such a way that inner cylindrical surface of said rotatable housing is sealingly tangent to rotor working chamber outer peripheral without any frictional contact; a crescent shape rotatable housing chamber formed by inner peripheral of housing and outer surface of the rotor being periodically divided into at most two working chambers by the pivoting vane and the common tangency point of two osculating surfaces, namely the rotor outer boundary and rotatable housing cylindrical inner peripheral; a plurality of working chambers formed depending on the rotational position of the pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable housing chamber, outer peripheral surface of the rotor and the side surface of the hinged arc vane; an inlet port formed in said rotatable housing for admitting ambient pressure fluid flows into a working chamber delimited by the rotor outer cylinder surface, rotatable housing inner cylindrical peripheral wall and arc vane side surface; an rotatable inlet port positioned so as to prevent said working fluid to bypass the working chambers and shortcut the inlet and outlet ports; a working cycle lasting for 360° clockwise or counterclockwise rotation of rotatable housing, wherein a new working cycle under the rotation of said housing is initiated every time the arc vane crosses the tangency point, the first working chamber admitting ambient pressure fluid from inlet port for entire duration of the first 360° rotation, wherein a second working cycle is defined in the consecutive 360° clockwise or counterclockwise rotation of said rotatable housing and said rotor, compressing the working fluid to high pressure in second working chamber by continuously diminishing chamber working volume; discharging said compressed fluid through exhaust port, wherein the maximum crescent shape volume of the compressor main chamber is sized to allow the outlet fluid pressure to reach desired high discharge pressure values; a periodic sequence of compressed fluid discharged from the outlet port with each rotation of the rotatable main housing in response to input driving torque and circumferential speed of said main rotatable housing; an outlet port equipped with a check-valve or a rotating valve synchronous with main housing shaft speed either mechanically or electrically, regulating the exhaust time and duration of the high pressure working fluid leaving from rotary compressor and thus preventing the said working fluid to bypass the working chambers and shortcut the inlet and outlet ports and strictly preventing any pressurized working fluid to enter back the working chamber from the exhaust port; a dynamic balance achieved by assembling and operating side-by-side twin/identical rotary compressors with separate inlet and exit ports, said twin compressors connected in such a way that one rotary compressor respective arc vane circumferential positions is 180° phase angle apart with respect to other twin compressor; radial or axial turbine blades rows attached on the outer periphery of rotatable housing of described rotary compressor so as to form turbo-rotary components to be used as part of turbojets, turbofans, turboprops and turboshaft engines; and electrical motor components attached on the outer periphery of rotatable housing of described rotary compressor so as to form a compact fluid energy input device.
 4. A nested multistage rotary compressor combining a plurality of radially nested (first/outer and second/inner) rotary compressors in such a way that the output of first/outer rotary compressor is the input of a second/inner rotary compressor, wherein the first and second rotary compressor comprising: a rotatable housing having a generally cylindrical main chamber, a generally cylindrical middle ring mounted eccentrically with respect to rotatable housing main chamber center and a generally cylindrical rotatable rotor mounted eccentrically with respect to rotatable middle ring, the rotatable housing chamber fully containing the rotatable middle ring and the rotatable middle ring fully containing the rotor; radially nested multistage rotary compressor further including: a generally cylindrical rotatable main housing free to revolve 360° around fixed axis center and a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotatable housing and a hinge movably connecting said vane to the rotatable middle ring; a generally cylindrical rotor free to revolve 360° around fixed eccentrically placed axis center, a single vane assembly comprised of an arched circular portion having a pivot axis fixed to rotor and a hinge movably connecting said vane to rotatable middle ring, said middle ring eccentrically placed axis center located closer to main rotatable housing axis center with respect to rotor axis center; a fixed shaft center rigidly connected to external fixed reference frame and a rotatable housing revolving 360° around said fixed shaft center; a fixed shaft center rigidly connected to eccentrically placed cylindrical fixed shaft extension and a middle ring, rotatably and circumferentially revolving 360° around said eccentrically placed cylindrical fixed shaft extension; a fixed shaft center rigidly connected to eccentrically placed cylindrical fixed axis extension and a rotor rotatably and circumferentially revolving 360° around said eccentrically placed axis extension, an eccentricity of rotor axis being larger than eccentricity of rotatable middle ring axis; air and/or fluidic journal and/or roller bearings provided between rotatable housing and fixed shaft center, between rotatable middle ring and fixed eccentric shaft axis and also between rotor and fixed eccentric rotor shaft axis to reduce rotational friction; an outer single arc vane element pivotally mounted to rotatable housing body and periodically extending sealingly from rotatable housing slot into eccentrically placed rotatable middle ring to divide the outer crescent shape volume into two consecutive working chambers, said rotatable housing body movably hinged to said outer arc vane in such a way that inner cylindrical surface of said rotatable housing is sealingly tangent to rotatable middle ring working chamber outer peripheral without any frictional contact; an inner single arc vane element pivotally mounted to rotor body and periodically extending sealingly from rotor slot into said rotatable middle ring to divide the inner crescent shape volume into two consecutive working chambers, said rotor movably hinged to said inner arc vane in such a way that outer cylindrical surface of said rotor is sealingly tangent to rotatable middle ring chamber inner peripheral without any frictional contact; an outer crescent shape main housing chamber formed by inner peripheral of main housing and outer surface of middle ring being periodically divided into at most two working chambers by the pivoting outer vane and the common tangency point of two osculating surfaces, namely the middle ring outer boundary and rotatable main housing cylindrical inner peripheral; an inner crescent shape middle ring chamber formed by inner peripheral of middle ring and outer surface of rotor being periodically divided into at most two working chambers by the pivoting inner vane and the common tangency point of two osculating surfaces, namely the rotor outer boundary and rotatable middle ring cylindrical inner peripheral; an inlet port for outer rotary compressor located at rotatable main housing, continuously admitting working fluid into outer rotary compressor, the outer arc vane preventing said working fluid to bypass the outer working chambers and shortcut outer compressor inlet and outlet ports; outer compressor first working chamber delimited by the rotatable housing inner cylindrical peripheral wall, middle ring cylindrical outer surface and arc vane side surface; a working cycle lasting for 360° counter-clockwise rotation of rotatable main housing, wherein a new working cycle under the rotation of said main housing is initiated every time the outer arc vane crosses the tangency point, wherein a first working chamber admitting ambient pressure fluid from inlet port of outer rotary compressor for entire duration of the first 360° rotation, a next working cycle defined in the consecutive 360° counterclockwise rotation of said rotatable middle ring and said rotor, further compressing the working fluid to higher pressure in a second working chamber by continuously diminishing chamber working volume and discharging said compressed fluid through outer rotary compressor exhaust port on the second/inner rotary compressor, the next working cycle defined in the consecutive 360° clockwise rotation of said eccentrically placed middle ring, inner rotor and inner arc vane assembly allowing further compression of working fluid now in fourth working chamber to discharge through inner compressor exhaust port, with maximum crescent shape volume of the outer compressor main chamber is sized to allow the radially nested multistage rotary compressor to achieve overall desired discharge pressure; a plurality of working chambers formed depending on the rotational position of the outer pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable main housing, outer peripheral surface of the middle ring and the side surface of the outer hinged arc vane; a plurality of working chambers formed depending on the rotational position of the inner pivoting vane, each of the said chambers, delimited by inner cylindrical peripheral surface of rotatable middle ring, outer peripheral surface of the rotor and the side surface of the inner hinged arc vane; a periodic sequence of compressed fluid discharged from the outlet port of inner rotary compressor with each rotation of the rotatable main housing in response to input driving torque and circumferential speed of said main rotatable housing; Inner compressor outlet port is also connected to rotor eccentrically placed fixed hollow axis center, said outlet port discharging high pressure working fluid; a periodic sequence of continuously compressed fluid discharged from outlet port of inner rotary compressor with each rotation of rotatable middle ring, rotor and inner arc vane assembly in response to input driving torque and circumferential speed of said main rotatable housing; a dynamic balance achieved by assembling and operating side-by-side twin/identical radially nested multistage rotary compressors with separate inlet and exit ports, said twin compressors connected in such a way that each compressor respective outer vane circumferential positions is 180° phase angle apart with respect to other twin compressor; radial or axial turbine blades attached on the outer periphery of rotatable housing of described, radially nested multistage rotary compressor so as to form turbo-rotary components to be used as part of turbojets, turbofans, turboprops and turboshaft engines; and electrical generators components attached on the outer periphery of rotatable housing of described radially nested multistage rotary expander so as to form a compact fluid energy recovery electrical generator device 